EP2306038B1 - Système à embrayage multi-disque - Google Patents

Système à embrayage multi-disque Download PDF

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Publication number
EP2306038B1
EP2306038B1 EP10251669.7A EP10251669A EP2306038B1 EP 2306038 B1 EP2306038 B1 EP 2306038B1 EP 10251669 A EP10251669 A EP 10251669A EP 2306038 B1 EP2306038 B1 EP 2306038B1
Authority
EP
European Patent Office
Prior art keywords
clutch
plate
pressure plate
pressure
friction plates
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP10251669.7A
Other languages
German (de)
English (en)
Other versions
EP2306038A2 (fr
EP2306038A3 (fr
Inventor
Yoshitsugu Gokan
Jun Miyazaki
Yoshinobu Shiomi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Honda Motor Co Ltd
Original Assignee
Honda Motor Co Ltd
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Filing date
Publication date
Application filed by Honda Motor Co Ltd filed Critical Honda Motor Co Ltd
Publication of EP2306038A2 publication Critical patent/EP2306038A2/fr
Publication of EP2306038A3 publication Critical patent/EP2306038A3/fr
Application granted granted Critical
Publication of EP2306038B1 publication Critical patent/EP2306038B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
    • F16D13/54—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member
    • F16D13/56—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member in which the clutching pressure is produced by springs only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
    • F16D13/54—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member
    • F16D13/56—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member in which the clutching pressure is produced by springs only
    • F16D2013/565—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member in which the clutching pressure is produced by springs only with means for releasing the clutch pressure in case of back torque

Definitions

  • the present invention relates to a multi-plate clutch system.
  • the invention relates to a multi-plate clutch system which includes: a clutch outer connected to an input member; a clutch inner connected to an output member; multiple driving friction plates engaged with the clutch outer in such a way as to be movable in an axial direction, and to be non-rotatable relative to the clutch outer; multiple driven friction plates interleaved with the driving friction plates, the driven friction plates being engaged with the clutch inner in such a way as to be movable in the axial direction and to be non-rotatable relative to the clutch inner; a pressure plate movable in the axial direction in order to cause the driving friction plates and the driven friction plates to frictionally engage with each other by bringing the driving friction plates and the driven friction plates into pressure contact with each other; a clutch spring for biasing the pressure plate in a direction in which the pressure plate brings the driving friction plates and the driven friction plates into pressure contact with each other; and at least one of an assist means and a slipper means, the assist means being for increasing a pressure-contact force of the pressure plate when torque changes for
  • Japanese Patent Application No. 2008-038954 discloses a multi-clutch system in which a pressure-contact force between driving friction plates and driven friction plates can be increased in such a way that: when torque changes for acceleration, the assist means retracts a clutch inner, and thus, in addition to the biasing force exerted on the clutch inner by the clutch spring, the retracting force is caused to work on the pressure plate.
  • the present invention has been made with the above-mentioned situation taken into consideration. It is an object of at least the preferred embodiments of the present invention to provide a multi-plate clutch system which is capable of performing an appropriate clutch connection while avoiding an abrupt clutch connection.
  • a multi-plate clutch system including: a clutch outer connected to an input member; a clutch inner connected to an output member; a plurality of driving friction plates engaged with the clutch outer in such a way as to be movable in an axial direction and to be non-rotatable relative to the clutch outer; a plurality of driven friction plates interleaved with the driving friction plates, the driven friction plates being engaged with the clutch inner in such a way as to be movable in the axial direction and to be non-rotatable relative to the clutch inner; a pressure plate movable in the axial direction in order to cause the driving friction plates and the driven friction plates to frictionally engage with each other by bringing the driving friction plates and the driven friction plates into pressure contact with each other; a clutch spring for biasing the pressure plate in a direction in which the pressure plate brings the driving friction plates and the driven friction plates into pressure contact with each other; and assist means for increasing a pressure-contact force of the pressure plate when torque for acceleration is changed, the
  • a slipper means for decreasing the pressure-contact force produced by the pressure plate when torque for deceleration is changed is installed between the output member and the clutch inner in such a way that, while operating, the slipper means moves the pressure plate in a direction in which the pressure plate decreases the pressure-contact force between the driving friction plates and the driven friction plates with the clutch inner being in intimate contact with the pressure plate.
  • the assist means includes: a spring configured to exert a spring force for biasing the clutch inner against a spring force of the clutch spring; and a cam mechanism configured to forcedly move the clutch inner against the biasing force of the spring to increase the pressure-contact force produced by the pressure plate when the torque for acceleration is changed.
  • the clutch inner includes an engagement cylinder part engaging the driven friction plates with its outer periphery, an insertion cylinder part coaxially inserted in the engagement cylinder part is provided to the pressure plate, a plurality of groove forming projecting parts in which spline grooves are respectively formed are provided to one of an inner periphery of the engagement cylinder part and an outer periphery of the insertion cylinder part, and a plurality of spline projecting parts engaged with the respective spline grooves are provided to the other of the inner periphery of the engagement cylinder part and the outer periphery of the insertion cylinder part.
  • the clutch inner and the pressure plate are provided with flat abutment parts extending along planes orthogonal to axes of the clutch inner and the pressure plate, respectively, in such a way that the flat abutment parts are in contact with each other when the clutch inner is brought into intimate contact with the pressure plate.
  • a plurality of groove forming projecting parts in which spline grooves are respectively formed are provided to one of the clutch inner and the pressure plate, a plurality of spline projecting parts engaged with the respective spline grooves are provided to the other of the clutch and the pressure plate, and the abutment parts are provided in such a way as to be unitarily continuous to the groove forming projecting parts and the spline projecting parts to extend inward from the groove forming projecting parts and the spline projecting parts in a radial direction.
  • the multiple spline projecting parts provided to the other of the clutch inner and the pressure plate are engaged with the spline grooves formed in the multiple groove forming projecting parts provided to the one of the clutch inner and the pressure plate, respectively.
  • the abutment parts extend inward in the radial direction from the groove forming projecting parts and the spline projecting parts. This makes it possible to reinforce the groove forming projecting parts and the spline projecting parts by thickening the perimeters of the groove forming projecting parts and the spline projecting parts.
  • a first oil passage for guiding oil to an engagement area between the spline grooves and the spline projecting parts is provided in the pressure plate in such a way as to penetrate the insertion cylinder part in a radial direction.
  • the slidability of the spline engagement area can be enhanced by supplying oil to the spline engagement area.
  • a second oil passage for guiding oil to an engagement area between the spline grooves and the spline projecting parts is provided in the pressure plate in such a way as to penetrate the insertion cylinder part in the axial direction.
  • sliding-contact surfaces are respectively provided to the clutch inner and the pressure plate in such a way as to be in sliding contact with each other, the sliding-contact surfaces being continuous to inner ends of the two abutment parts extending in the radial directions of the clutch inner and the pressure plate, the sliding-contact surfaces each being formed in the shape of an arc about a centre axis line of the clutch inner.
  • This arrangement makes the displacement of the axes of the clutch inner and the pressure plate less likely to occur, and accordingly makes it possible to make the slide in the spline engagement area far smoother.
  • spaces are formed between the spline projecting parts and one of an inner periphery of an engagement cylinder part and an outer periphery of an insertion cylinder part, as well as between the groove forming projecting parts and the other of the inner periphery of the engagement cylinder part and the outer periphery of the insertion cylinder part, respectively.
  • the sliding contact between the sliding-contact surfaces prevents the displacement of the axes of the clutch inner and the pressure plate, and inhibits increase in the area of the slide in the spline engagement area. Furthermore, the use of the spaces as passages through which oil flows can enhance the slidability and lubricity in the spline engagement area.
  • a main shaft 11 of the embodiment corresponds to the output member, and a primary driven gear 16 corresponds to the input member.
  • a primary speed reducing device 12 a damper spring 13 and a multi-plate clutch system 14A are installed between a crank shaft (not illustrated) of, for example, a motorcycle engine and a main shaft 11 of a gear transmission system (not illustrated).
  • the primary speed reducing device 12 includes: a primary driving gear 15 provided to the crank shaft; and a primary driven gear 16 in mesh with the primary driving gear 15.
  • the primary driven gear 16 is supported by the main shaft 11 in such a way that the primary driven gear 16 is rotatable relative to the main shaft 11.
  • the primary driven gear 16 is an input member
  • the main shaft 11 is an output member.
  • the multi-plate clutch system 14A which is a wet-type, includes; a clutch outer 17 connected to the primary driven gear 16, which serves as an input member, with the damper spring 13 in between; a clutch inner 18A which includes an engagement cylinder part 18a and an annular support wall 18b formed integrally therewith, the engagement cylinder part 18a coaxially placed inside the clutch outer 17, and the annular support wall 18b extending radially inwardly from an inner surface of a middle portion of the engagement cylinder part 18a; multiple driving friction plates 19 which are engaged with the clutch outer 17 in such a way as to be relatively non-rotatable; multiple driven friction plates 20 which are arranged to be interleaved with the driving friction plates 19 and are engaged with an outer periphery of the engagement cylinder part 18a of the clutch inner 18A in such a way as to be relatively non-rotatable; a pressure bearing plate 21, serving as a clamp pressure plate, which is fixed to the main shaft 11 in such a way as to face
  • the clutch outer 17 includes: a cylinder part 17a coaxially surrounding an engagement cylinder part 18a of the clutch inner 18A; and an integrally formed end wall part 17b connected to an end portion of the cylinder part 17a on the primary driven gear 16 side.
  • the clutch outer 17 is shaped like a cup, and has an opening facing away from the primary driven gear 16. Outer peripheral portions of the respective multiple driving friction plates 19 are engaged with an inner periphery of the cylinder part 17a in such a way that the multiple driving friction plates 19 are movable in the axial direction and are relatively non-rotatable.
  • An annular step part 11a facing the multi-plate clutch system 14A is formed in a portion of an outer periphery of the main shaft 11, the portion corresponding to the primary speed reducing device 12.
  • a cylinder-shaped sleeve 28, which is fitted to the outer periphery of the main shaft 11, has an end portion, which is located on a side away from the multi-plate clutch system 14A, and which is in contact with the annular step part 11a.
  • a needle bearing 29 is interposed between an outer periphery of this sleeve 28 and an inner periphery of the primary driven gear 16.
  • This centre cam plate 30 includes: a cylinder-shaped boss part 30a which is spline-engaged with the outer periphery of the main shaft 11; and an integrally formed disc part 30b which is arranged in a plane orthogonal to the axial direction of the main shaft 11, the disc part 30b extending radially outward from an axially central portion of the boss part 30a.
  • the pressure bearing plate 21 is generally disc-shaped. An inner peripheral portion of the pressure bearing plate 21 is spline-engaged with the outer periphery of the main shaft 11 in such a way as to be interposed between a plate-like ring-shaped pressing plate 31 and one end portion of the boss part 30a. The pressing plate 31 is in contact with the end portion of the sleeve 28 which is nearer the multi-plate clutch system 14A.
  • a spring bearing member 32 is spline-engaged with the main shaft 11, and the boss part 30a is sandwiched between the spring bearing member 32 and an inner periphery of the pressure bearing plate 21.
  • a nut 33 is screwed to the main shaft 11, so as to locate the spring bearing member 32 between the nut 33 and the boss part 30a.
  • the pressure plate 22 includes an annular pressing part 22a and an integrally formed insertion cylinder part 22b.
  • the annular pressing part 22a sandwiches the driving friction plates 19 and the driven friction plates 20 with the pressure bearing plate 21.
  • the insertion cylinder part 22b is installed with the pressing part 22a in such a way as to be inserted into the engagement cylinder part 18a of the clutch inner 18A.
  • the insertion cylinder part 22b is formed to have steps in such a way that the diameter thereof becomes smaller toward the extremity thereof in a stepwise fashion.
  • the clutch spring 23 is a disc spring, provided between the spring bearing member 32 fixed to the main shaft 11 and the pressure plate 22. A radially inner peripheral portion of this clutch spring 23 is in contact with and engaged with the spring bearing member 32 from the centre cam plate 30 side. A radially outer peripheral portion of the clutch spring 23 is in contact with an annular step part 34, with a ring-shaped sliding-contact plate 35 in between.
  • the annular step part 34 is provided to the insertion cylinder part 22b of the pressure plate 22, and faces away from the centre cam plate 30.
  • the configuration is such that the pressure plate 22 is biased by the clutch spring 23 in a direction in which the pressure plate 22 puts the multi-plate clutch system 14A into a connected condition, by bringing the driving friction plates 19 and the driven friction plates 20 into pressure contact with each other so as to cause friction engagement therebetween.
  • the clutch inner 18A is movable relative to the main shaft 11 in the axial direction of the main shaft 11.
  • the clutch inner 18A and the pressure plate 22 (which is a different member from the clutch inner 18A) are connected together so as to be non-rotatable relative to each other and so as to be capable of being separated from each other in the axial direction in such a way that, when the assist means 24 increases the pressure-contact force of the pressure plate 22, the pressure plate 22 is moved in the direction to bring the driving friction plates 19 and the driven friction plates 20 into pressure contact with each other while the clutch inner 18A is moved relative to the pressure plate 22 in the same direction in such a way as to be detached from the pressure plate 22.
  • the insertion cylinder part 22b of the pressure plate 22 is inserted in an end portion of the engagement cylinder part 18a of the clutch inner 18A, the end portion being on the pressure plate 22 side.
  • Multiple groove forming projecting parts 37 are provided to one of the inner periphery of the engagement cylinder part 18a and the outer periphery of the insertion cylinder part 22b (the inner periphery of the engagement cylinder part 18a in this embodiment).
  • Multiple spline projecting parts 39 are provided to the other of the inner periphery of the engagement cylinder part 18a and the outer periphery of the insertion cylinder part 22b (the outer periphery of the insertion cylinder part 22b in this embodiment).
  • Spline grooves 38 which engage with the spline projecting parts 39 are formed in the groove forming projecting parts 37, respectively.
  • a first oil passage 40 for guiding oil to engagement parts between the spline grooves 38 and the spline projecting parts 39 is formed in the insertion cylinder part 22b of the pressure plate 22 in such a way as to penetrate the insertion cylinder part 22b in the radial direction.
  • a second oil passage 41 for guiding oil to the engagement parts between the spline grooves 38 and the spline projecting parts 39 is formed in the pressing part 22a of the pressure plate 22 in such a way as to penetrate the pressing part 22a in the axial direction.
  • the multi-plate clutch system 14A is covered with an engine cover 42 provided to the engine.
  • One end portion of an operation shaft 43 is fitted in the engine cover 42 in such a way as to be movable in the axial direction, and the other end portion of the operation shaft 43 is fitted in the main shaft 11 coaxially and slideably.
  • An inner peripheral portion of a disc-shaped lifter 45 is held by a middle portion of this operation shaft 43 with a clutch bearing 44 interposed in between.
  • An outer periphery of this lifter 45 is in contact with, and engaged with, a stop ring 46, which is attached to the inner periphery of the pressing part 22a of the pressure plate 22 from the clutch spring 23 side, with a ring-shaped sliding-contact plate 69 being interposed in between.
  • a control shaft 47 for switching between disconnection and connection of the multi-plate clutch system 14A is rotatably and movably supported by the engine cover 42.
  • a lever 48 is provided at an end portion of the control shaft 47 which projects from the engine cover 42.
  • the said one end portion of the operation shaft 43 is engaged with an inner end portion of the control shaft 47 in such a way that the operation shaft 43 moves in the axial direction in response to rotation of the control shaft 47.
  • the assist means 24 moves the pressure plate 22 closer to the pressure bearing plate 21 as the driving power inputted from the primary driven gear 16 becomes larger.
  • the assist means 24 includes: a spring 48 for exerting a spring force for biasing the clutch inner 18A against a spring force of the clutch spring 23; and a cam mechanism 49 for forcedly moving the clutch inner 18A against the biasing force of the spring 48 in order to assist the pressure plate 22 in increasing the pressure-contact force when torque changes for acceleration.
  • the cam mechanism 49 is disposed between the disc part 30b of the centre cam plate 30 fixed to the main shaft 11 and an assist cam plate 50, whose inner peripheral portion is slidingly supported by the boss part 30a of the centre cam plate 30 in such a way as to face one surface of the disc part 30b.
  • An outer periphery of the assist cam plate 50 is spline-engaged with the inner periphery of the engagement cylinder part 18a of the clutch inner 18A.
  • multiple (in this case, three) first depressed cams 51 are made in the one surface of the disc part 30b of the centre cam plate 30 in such a way as to be equispaced in the circumferential direction.
  • multiple (in this case, three) first projecting cams 52 which constitute the cam mechanism 49 in cooperation with the first depressed cams 51, are provided projecting from a surface of the assist cam plate 50 on the side facing disc part 30b.
  • a stop ring 55 is located in an annular depressed part 54 formed in the inner periphery of the engagement cylinder part 18a of the clutch inner 18A.
  • the stop ring 55 is in contact with, and engages with, an outer periphery of the end surface of the assist cam plate 50 distant from the disc part 30b.
  • the spring 48 is a disc spring whose radially inner peripheral portion is in contact with, and supported by, the radially inner peripheral portion of the pressure bearing plate 21 with a ring-shaped sliding-contact plate 53 interposed in between.
  • a radially outer periphery of this spring 48 is in contact with an annular bearing member 56 which is in contact with one of the end surfaces of the assist cam plate 50 which is situated further from the centre cam plate 30.
  • the bearing member 56 is placed contiguous to an inner periphery of the stop ring 55.
  • An outer diameter of the bearing member 56 is set to be equal to an inner diameter of the stop ring 55 as put in the annular depressed part 54.
  • An axial length L1 of the bearing member 56 is set to be larger than an axial width L2 of the opening of the annular depressed part 54.
  • the slipper means 25 moves the clutch inner 18A in the direction in which the pressure plate 22 is caused to come away from the pressure bearing plate 21 when torque changes for deceleration.
  • the slipper means 25 is made up by providing a cam mechanism 58 between the centre cam plate 30 and a slipper cam plate 57, whose inner peripheral portion is slidingly supported by the boss part 30a of the centre cam plate 30 in such a way that the slipper cam plate 57 faces the other surface of the disc part 30b of the centre cam plate 30.
  • An outer periphery of the slipper cam plate 57 is spline-engaged with the inner periphery of the engagement cylinder part 18a of the clutch inner 18A.
  • multiple (in this case three) second depressed cams 59 are formed in the other surface of the disc part 30b of the centre cam plate 30, equispaced circumferentially, in such a way that each of the second depressed cams 59 is located in a centre portion between the corresponding two of the first depressed cams 51.
  • multiple (in this case three) second projecting cams 60 which constitute the cam mechanism 58 in cooperation with the second depressed cams 59, are provided projecting from a surface of the slipper cam plate 57 facing the disc part 30b.
  • An outer periphery of the end surface of the slipper cam plate 57 distant from the disc part 30b is in contact with the annular support wall 18b of the clutch inner 18A, with a ring-shaped sliding-contact plate 61 being interposed in between.
  • the assist cam plate 50 and the slipper cam plate 57 facing the respective opposite sides of the disc part 30b of the centre cam plate 30 are fixed to the clutch inner 18A in such a way as to be held between the annular support wall 18b provided to the clutch inner 18A and the stop ring 55 in the inner periphery of the engagement cylinder part 18a of the clutch inner 18A.
  • a guide ring 62 interposed between the assist cam plate 50 and the slipper cam plate 57 is placed between an outer periphery of the disc part 30b of the centre cam plate 30 and the inner periphery of the engagement cylinder part 18a of the clutch inner 18A.
  • a width W1 of the spline engagement of the slipper cam plate 57 with the clutch inner 18A is set to be smaller than a width W2 of the spline engagement of the assist cam plate 50 (the other cam plate) with the clutch inner 18A.
  • the slipper cam plate 57 is closer to the annular support wall 18b provided to the clutch inner 18.
  • the clutch inner 18A and the pressure plate 22 are provided with flat abutment parts 63, 64 which extend orthogonal to the axes of the clutch inner 18A and the pressure plate 22 in such a way that the flat abutment parts 63, 64 are in contact with each other, respectively.
  • the abutment part 63 is formed in such a way as to unitarily continue to the multiple groove forming projecting parts 37 in the inner periphery of the engagement cylinder part 18a of the clutch inner 18A, and concurrently to extend inward in the radial direction.
  • the other abutment part 64 is formed in the middle of the insertion cylinder part 22b in such a way as to unitarily continue to the spline projecting parts 39, and to extend inward in the radial direction.
  • the abutment part 63 of the clutch inner 18A is biased toward the pressure plate 22 by the spring 48 and is in contact with the abutment part 64 of the pressure plate 22. Accordingly, a biasing force in the reverse direction, which is produced by the spring 48 to offset the biasing force of the clutch spring 23, acts on the pressure plate 22.
  • cam side surfaces of the first projecting cams 52 are brought into contact with cam side surfaces of the first depressed cams 51, respectively.
  • the cam mechanism 49 subjects the assist cam plate 50 to a force which causes the assist cam plate 50 to detach from the disc part 30b of the centre cam plate 30.
  • the clutch inner 18A (to which the assist cam plate 50 is fixed) moves in a direction in which the clutch inner 18A detaches from the pressure plate 22, and the bearing member 56 in contact with the assist cam plate 50 moves in a direction which decreases the spring force of the spring 48.
  • the cam mechanism 58 of the slipper means 25 moves the slipper cam plate 57 (which is fixed to the clutch inner 18A) in a direction in which the slipper cam plate 57 detaches from the centre cam plate 30.
  • This movement of the slipper cam plate 57 brings the abutment part 63 of the clutch inner 18A into intimate contact with the abutment part 64 of the pressure plate 22.
  • the pressure plate 22 moves in a direction which decreases the pressure-contact force between the driving friction plates 19 and the driven friction plates 20.
  • the clutch inner 18A and the pressure plate 22 are provided with respective sliding-contact surfaces 65, 66 in such a way that the surfaces 65, 66 are in sliding contact with each other.
  • the sliding-contact surfaces 65, 66 continue to inner ends of the two abutment parts 63, 64 which extend in the radial directions of the clutch inner 18A and the pressure plate 22, respectively.
  • the sliding-contact surfaces 65, 66 are formed in the shape of an arc about the centre axis line of the clutch inner 18A. In other words, an inner peripheral surface of the annular support wall 18b provided to the clutch inner 18A is in sliding contact with the insertion cylinder part 22b of the pressure plate 22.
  • the sliding-contact surface 66 in sliding contact with the sliding-contact surface 65 formed in the inner periphery of the annular support wall 18b is formed in an outer periphery of the extremity of the insertion cylinder part 22b.
  • a space 67 is formed between the spline projecting parts 39 and the inner periphery of the engagement cylinder part 18a, and a space 68 is formed between the groove forming projecting part 37 and the outer periphery of the insertion cylinder part 22b.
  • the guide ring 62 is fixed to the clutch inner 18A by the interposition of the guide ring 62 between the assist cam plate 50 and the slipper cam plate 57.
  • An inner periphery of this guide ring 62 is in sliding contact with an outer periphery of the disc part 30a of the centre cam plate 30.
  • multiple oil holes 70 for connecting inner and outer sides of the engagement cylinder part 18a of the clutch inner 18A are made in the engagement cylinder part 18a.
  • Oil grooves 71 for causing oil to flow between the guide ring 62 and the assist cam plate 50 as well as between the guide ring 62 and the slipper cam plate 57 are made in the two sides of the guide ring 62.
  • a central passage 72 for guiding oil is coaxially provided in the main shaft 11.
  • Oil passages 73 whose ends communicate with the central passage 72 are made in the sidewall of the main shaft 11 at a position which substantially corresponds to the axially central portion of the boss part 30a of the centre cam plate 30.
  • Oil supplying passages 74 for supplying oil from the oil passages 73 to the first projecting cams 52 of the assist cam plate 50 and the second projecting cams 60 of the slipper cam plate 57 are made in the boss part 30a of the centre cam plate 30 in such a way as to be oriented in a direction which tilts to the centre axis line of the assist cam plate 50 and slipper cam plate 57.
  • Orifices 75 are installed in the respective oil supplying passages 74.
  • the multiple first depressed cams 51 are made in one surface of the disc part 30b of the centre cam plate 30, and the multiple second depressed cams 59 are made in the other surface of the disc plate 30b of the centre cam plate 30.
  • Oil discharging passages 76 for guiding oil to a sliding-contact area between an outer periphery of the centre cam plate 30 and an inner periphery of the guide ring 62 are provided in outer peripheral edge portions of the first depressed cams 51.
  • Oil discharging passages 77 for guiding oil to the sliding-contact area between the outer periphery of the centre cam plate 30 and the inner periphery of the guide ring 62 are provided in outer peripheral edge portions of the second depressed cams 59 (see Fig. 3 ).
  • those oil discharging passages 76, 77 are formed as notches made in the outer peripheral edge portions of the first and second depressed cams 51, 59.
  • at least areas in which the first and second depressed cams 51, 59 are placed, as well as the notches in the outer peripheral edge portions of the first and second depressed cams 51, 59, are formed by forging, for example.
  • contact surfaces of the first depressed cams 51 and the first projecting cams 52 which constitute the cam mechanism 49 provided between the centre cam plate 30 and the assist cam plate 50, are formed in such a way that the contact surfaces of the first depressed cams 51 and the contact surfaces of the first projecting cams 52 are brought into contact with each other when the assist cam plate 50 rotates relative to the centre cam plate 30.
  • first projecting cams 52 are provided in the surface of the assist cam plate 50 which faces the disc part 30b of the centre cam plate 30.
  • multiple (in this case three) first depressed parts 80 are formed in such a way that each two neighbouring first depressed parts 80 are placed respectively in the two sides of the corresponding one of the first projecting cams 52.
  • the second projecting cams 60 are provided in the surface of the slipper cam plate 57 which faces the disc part 30b of the centre cam plate 30.
  • multiple (in this case three) second depressed parts 81 are formed in such a way that each two neighbouring second depressed parts 81 are placed respectively in the two sides of the corresponding one of the second projecting cams 60.
  • the spring 48, the bearing member 56, the assist cam plate 50, the guide ring 62, the centre cam plate 30, the slipper cam plate 57 and the sliding-contact plate 61 are inserted in the engagement cylinder part 18a of the clutch inner 18A from the pressure bearing plate 21 side.
  • the spring 48, the bearing member 56, the assist cam plate 50, the guide ring 62, the centre cam plate 30, the slipper cam plate 57 and the sliding-contact plate 61 are beforehand assembled into an assembled body 84.
  • An annular step part 85b for holding the assembled body 84 between the annular step part 85b and the pressure bearing plate 21 is provided to a rod-like holding tool 85 penetrating the assembled body 84 in such a way that an small-diameter end part 85a of the holding tool 85 is fitted in the pressure bearing plate 21, as shown by the chain line in Fig. 2 .
  • the clutch inner 18A is fitted to the assembled body 84 in such a way that the assembled body 84 is covered with the clutch inner 18A while held between the holding tool 85 and the pressure bearing plate 21.
  • the clutch inner 18A (which is movable in the axial direction of the main shaft 11) and the pressure plate 22 (which is a different member from the clutch inner 18A) are connected together so as to be non-rotatable relative to each other and so as to be capable of being separated from each other in the axial direction in such a way that, when the assist means 24 increases the pressure-contact force of the pressure plate 22, the pressure plate 22 is moved in the direction to bring the driving friction plates 19 and the driven friction plates 20 into pressure contact with each other while the clutch inner 18A is moved relative to the pressure plate 22 in the same direction in such a way as to be detached from the pressure plate 22.
  • the slipper means 25 is placed between the clutch inner 18A and the main shaft 11 in order that, when torque changes for deceleration, the slipper means 25 can decrease the pressure-contact force produced by the pressure plate 22 by: bringing the clutch inner 18A in intimate contact with the pressure plate 22; and thus causing the pressure plate 22 to move in the direction in which the pressure plate 22 decreases the pressure-contact force between the driving friction plates 19 and the driven friction plates 20.
  • the slipper means 25 decreases the pressure-contact force produced by the pressure plate 22 in response to the change in the torque for deceleration, back torque can be blocked instantaneously. Thereby, when assisted, an appropriate clutch connection can be achieved, and the back torque limiter capability can be secured as before.
  • the assist means 24 includes: the spring 48 configured to exert a spring force for biasing the clutch inner 18A against the spring force of the clutch spring 23; and the cam mechanism 49 configured to forcedly move the clutch inner 18A against the biasing force of the spring 48 in order that the pressure-contact force of the pressure plate 22 can be increased when torque changes for acceleration.
  • the spring 48 configured to exert a spring force for biasing the clutch inner 18A against the spring force of the clutch spring 23
  • the cam mechanism 49 configured to forcedly move the clutch inner 18A against the biasing force of the spring 48 in order that the pressure-contact force of the pressure plate 22 can be increased when torque changes for acceleration.
  • the clutch inner 18A includes the engagement cylinder part 18a which engages the driving friction plates 20 at its outer periphery.
  • the insertion cylinder part 22b coaxially inserted in the engagement cylinder part 18a is provided in the pressure plate 22, the multiple groove forming projecting parts 37 are made in the inner periphery of the engagement cylinder part 18a in order that spline grooves 38 can be formed in the respective groove forming projecting parts 37, and the multiple spline projecting parts 39 engaged with the respective spline grooves 38 are made in the outer periphery of the insertion cylinder part 22b.
  • the clutch inner 18A and the pressure plate 22 are provided with the flat abutment parts 63, 64, which extend along planes orthogonal to the axes of the clutch inner 18A and the pressure plate 22, respectively, in such a way that the flat abutment parts 63, 64 come in contact with each other when the clutch inner 18A is brought into intimate contact with the pressure plate 22.
  • the multiple groove forming projecting parts 37 are made in the clutch inner 18A in such a way that the spline grooves 38 are respectively formed in the groove forming projecting parts 37; and the multiple spline projecting parts 39 to be engaged with the respective spline grooves 38 are provided in the pressure plate 22.
  • the abutment parts 63, 64 extend inwards in the radial direction from the groove forming projecting parts 37 and the spline projecting parts 39 in such a way as to unitarily continue to the groove forming projecting parts 37 and the spline projecting parts 39. This makes it possible to reinforce the groove forming projecting parts 37 and the spline projecting parts 39 by thickening the perimeters of the groove forming projecting parts 37 and the spline projecting parts 39.
  • the first oil passage 40 for guiding the oil to the engagement area between the spline grooves 38 and the spline projecting parts 39 is made in the pressure plate 22 in such a way as to penetrate the insertion cylinder part 22b in the radial direction. This makes it possible to enhance the slidability of the spline engagement area by supplying the oil to the spline engagement area.
  • the second oil passage 41 for guiding the oil to the engagement area between the spline grooves 38 and the spline projecting parts 39 is made in the pressure plate 22 in such a way as to penetrate the pressing part 22a of the pressure plate 22 in the radial direction. This makes it possible to enhance the slidability of the spline engagement area by supplying the oil to the spline engagement area in the longitudinal direction of the spline grooves 38 and the spline protruding parts 39.
  • the clutch inner 18A and the pressure plate 22 are provided with the sliding-contact surfaces 65, 66, which continue to the inner ends of the two abutment parts 63, 64 extending in the clutch inner 18A and the pressure plate 22 in their radial directions, and which are formed in the shape of an arc about the centre axis line of the clutch inner 18A, in such a way that the sliding-contact surfaces 65, 66 are brought into sliding contact with each other, respectively. Since these sliding-contact surfaces 65, 66 are brought into sliding contact with each other, the axis of the clutch inner 18A and the axis of the pressure plate 22 become less likely to be displaced from each other. This makes it possible to make the slide in the spline engagement area far smoother.
  • the space 67 is formed between the spline projecting parts 39 and the inner periphery of the engagement cylinder part 18a, and the space 68 is formed between the groove forming projecting parts 37 and the outer periphery of the inserting cylinder part 22b.
  • the assist means 24 includes the centre cam plate 30 and the assist cam plate 50 which face each other in the axial direction.
  • the assist cam plate 50 is inserted in, and engaged with, the clutch inner 18A in such a way that the assist cam plate 50 is non-rotatable relative to the clutch inner 18A.
  • the stop ring 55 engaged with the assist cam plate 50 is put in the inner periphery of the engagement cylinder part 18a of the clutch inner 18A in order that the stop ring 55 can block the assist cam plate 50 from moving relative to the clutch inner 18A in such an axial direction that the assist cam plate 50 would detach from the centre cam plate 30.
  • the fixation of the assist cam plate 50 to the clutch inner 18A can be achieved by fixing the assist cam plate 50 to the clutch inner 18A by use of the stop ring 55 without creating an unbalance in attaching the assist cam plate 50 to the clutch inner 18A in the circumferential direction while inhibiting increase in the number of parts, weight and costs, as compared with the conventional fixing structure using bolts.
  • the spring 48 included in the assist means 24 biases the clutch inner 18A in the axial direction with the assist cam plate 50 being interposed in between.
  • the annular bearing member 56 receiving the end portion of the spring 48 on the clutch inner 18A side, is placed contiguous to the inner periphery of the stop ring 55. For this reason, it is possible to prevent the stop ring from coming off by use of the bearing member 56. This eliminates the need for a specialized member for preventing the stop ring from coming off, and thus can contribute to reduction in the number of parts.
  • the annular depressed part 54 for accommodating the stop ring 55 is made in the inner periphery of the engagement cylinder part 18a of the clutch inner 18A, and the bearing member 56 is formed in such a way as to have an outer diameter which is equal to the inner diameter of the stop ring 55 accommodated in the annular depressed part 54. Accordingly, the bearing member 56 is fitted to the stop ring 55, and thus it is possible to securely prevent the stop ring 55 from coming off.
  • the axial length L1 of the bearing member 56 is set to be larger than the axial width L2 of the opening of the annular depressed part 54.
  • the multi-plate clutch system 14A includes both the assist means 24 and the slipper means 25.
  • the centre cam plate 30 is fixed to the main shaft 11.
  • the assist cam plate 50 and the slipper cam plate 57 are opposed to the two sides of the disc part 30b of the centre cam plate 30.
  • the assist cam plate 50 and the slipper cam plate 57 are fixed to the clutch inner 18A in such a way as to be held between the annular support wall 18b provided to the clutch inner 18A and the stop ring 55. For this reason, the fixing of the assist cam plate 50 and the slipper cam plate 57 to the clutch inner 18A can be achieved by the single stop ring 55. Accordingly, it is possible to reduce parts in number.
  • the annular guide ring 62 is interposed between the assist cam plate 50 and the slipper cam plate 57.
  • This guide ring 62 is placed between the outer periphery of the centre cam plate 30 and the inner periphery of the clutch inner 18A. For this reason, increase in the number of parts needed for the structure in which the assist cam plate 50 and the slipper cam plate 57 are fixed to the clutch inner 18A by use of the single stop ring 55 can be inhibited by interposing the annular guide ring 62 used for holding the clutch inner 18A with the centre cam plate 30, between the assist cam plate 50 and the slipper cam plate 57.
  • the outer peripheries of the assist cam plate 50 and the slipper cam plate 57 are spline-engaged with the inner periphery of the engagement cylinder part 18a of the clutch inner 18A.
  • the width W1 of the spline engagement of the slipper cam plate 57, which is placed on the annular support wall 18b side out of the assist cam plate 50 and the slipper cam plate 57, with the clutch inner 18A is set smaller than the width W2 of the spline engagement of the assist cam plate 50 with the clutch inner 18A.
  • the inner peripheral surface of the annular support wall 18b provided to the clutch inner 18A is in sliding contact with the pressure plate 22. For this reason, it is possible to prevent the displacement of the axes of the clutch inner 18A and the pressure plate 22, since the clutch inner 18A is supported by the pressure plate 22.
  • the assist means 24 includes the centre cam plate 30 and the assist cam plate 50 which are opposed to each other in the axial direction.
  • the slipper means 25 includes: the centre cam plate 30 which is common between the slipper means 25 and the assist means 24; and the slipper cam plate 57 which is opposed to the centre cam plate 30 in the axial direction.
  • the guide ring 62 whose inner peripheral surface is in sliding contact with the outer peripheral surface of the centre cam plate 30 is fixed to the engagement cylinder part 18a of the clutch inner 18A.
  • the oil discharging passages 76, 77 for guiding the oil to the sliding-contact area between the centre cam plate 30 and the guide ring 62 are made in the outer peripheral edge portions of the first and second depressed cams 51, 59 provided respectively in the two surfaces of the disc part 30b of the centre cam plate 30.
  • the oil discharging passages 76, 77 are formed as notches made in the outer peripheral edge portions of the first and second depressed cams 51, 59. For this reason, it is possible to form the oil discharging passages 76, 77 with a simple structure.
  • the simple structure can enhance the lubricity of the sliding-contact area.
  • the depressions of the first and second depressed cams 51, 59 can be made shallow in depth by making notches in the outer peripheral edge portions of the first and second depressed cams 51, 59. This inhibits the amount of deformation of the parts during their pressing, and thus inhibits defective pressed products from being produced. Accordingly, the precision can be enhanced.
  • the contact surfaces of the first depressed cams 51 and the first projecting cams 52, which constitute the cam mechanism 49 provided between the centre cam plate 30 and the assist cam plate 50, as well as the contact surfaces of the second depressed cams 59 and the second projecting cams 60, which constitute the cam mechanism 58 provided between the centre cam plate 30 and the slipper cam plate 57, are formed in order to come into contact with each other when the assist cam plate 50 and the slipper cam plate 57 rotate relative to the centre cam plate 30.
  • the oil discharging passages 76, 77 are provided to only the edge portion of the outer periphery of the disc part 30b of the centre cam plate 30.
  • first depressed parts 80 are formed in the assist cam plate 50 in such a way that each two neighbouring first depressed parts 80 are respectively situated in the two sides of the corresponding one of the first projecting cams 52.
  • the second depressed parts 81 are formed in the slipper cam plate 57 in such a way that each two neighbouring second depressed parts 81 are respectively situated in the two sides of the corresponding one of the second projecting cams 62. For this reason, oil supplied to each of the first projecting cams 52 can be captured by, and held in, the corresponding two of the first depressed parts 80 which are respectively situated in the two sides of the first projecting cam 52.
  • Oil supplied to each of the second projecting cams 60 can be captured by, and held in, the corresponding two of the second depressed parts 81 which are respectively situated in the two sides of the second projecting cam 60. Thereby, it is possible to secure oil which is sufficiently distributed to the first and second projecting cams 52, 60. This makes it possible to enhance the lubricity between the first depressed cams 51 and the first projecting cams 52, as well as between the second depressed cams 59 and the second projecting cams 60.
  • the outer peripheral edge portions of the first and second depressed parts 80, 81 are formed in such a way as to curve toward the sliding-contact area between the centre cam plate 30 and the guide ring 62. For this reason, oil accumulated in the first and second depressed cams 51, 59 can be actively supplied to the sliding-contact areas. Accordingly, it is possible to enhance the lubricity.
  • the oil supplying passages 74 for supplying oil to the first projecting cams 52 of the assist cam plate 50 and the second projecting cams 60 of the slipper cam plate 57 are made in the boss part 30a of the centre cam plate 30 in such a way as to be oriented in a direction which tilts to the centre axis line of the assist cam plate 50 and slipper cam plate 57. For this reason, oil can be injected to the gaps between the first depressed cams 51 and the first projecting cams 52, as well as the gaps between the second depressed cams 59 and the second projecting cams 60, which need lubricity most. This makes it possible to prevent lack of lubricity which could otherwise occur due to shortage of oil.
  • orifices 75 are installed in the respective oil supplying passages 74. For this reason, oil can be injected with a high pressure, sprayed and spread to the first and second projecting cams 52, 60. Thereby, the overall lubricity can be enhanced between the first depressed cams 51 and the first projecting cams 52, as well as between the second depressed cams 59 and the second projecting cams 60.
  • oil discharging passages 86 for discharging oil to the sliding-contact area between the inner periphery of the guide ring 62 and the outer periphery of the disc part 30b of the centre cam plate 30 are formed in outer peripheral edge portions of the first depressed cams 51 provided in one surface of the disc part 30b of the centre cam plate 30 which is common between the assist means 24 and the slipper means 25 included in this multi-plate clutch system 14B, respectively.
  • similar oil discharging passages (not illustrated) are formed in outer peripheral edge portions of the second depressed cams 59 provided in the other surface of the disc part 30b.
  • the oil discharging passages 86 are made in each of the first and second depressed cams 51, 59 by providing therein through-holes each connecting the inner surface and outer surface of the corresponding one of the outer peripheral edge portions of the first and second depressed cams 51, 59. For this reason, oil inside the first and second depressed cams 51, 59 can be securely supplied to the sliding-contact area between the inner periphery of the guide ring 62 and the outer periphery of the disc part 30b of the centre cam plate 30, regardless of the heights of the peripheral edge portions of the first and second depressed cams 51, 59.
  • a clutch inner 18B included in this multi-plate clutch system 14C includes: an engagement cylinder part 18a which engages the driven friction plates 20 with its outer periphery; and an integrally formed annular middle wall 18c projecting radially inwards from an inner periphery of a middle portion of the engagement cylinder part 80a.
  • An inner periphery of the annular middle wall 18c is in sliding contact with the outer periphery of the centre cam plate 30 which is common between the assist means 24 and the slipper means 35.
  • the stop rings 55, 87 engaged with the assist cam plate 50 and slipper cam plate 57 from the opposite sides from the annular middle wall 18c are put on the assist cam plate 50 and the slipper cam plate 57 between which the annular middle wall 18c is interposed, respectively.
  • the stop ring 55 whose inner periphery is contacted by the bearing member 56 for receiving the spring 48 is formed with a circular cross section.
  • the other stop ring 87 is formed with a rectangular cross section.
  • first and second depressed cams 51, 59 are provided in the two sides of the disc part 30b of the centre cam plate 30 as in the first embodiment.
  • oil discharging passages 76, 77 for guiding oil to the sliding-contact area between the centre cam plate 30 and the clutch inner 18B are provided in the outer peripheral edge portions of the depressed cams 51, 59, as in the first embodiment.
  • the third embodiment can achieve the fixing structures for the assist cam plate 50 and the slipper cam plate 57 in a smaller size with low costs by use of the stop rings 55, 87 in such a way that: the annular middle wall 18c provided in the clutch inner 18B is interposed between the assist cam plate 50 and the slipper cam plate 57 which are opposed to the two sides of the centre cam plate 30; the stop rings 55, 87 engaged with the assist cam plate 50 and the slipper cam plate 57 from the opposite sides from the annular middle wall 18c are attached to the clutch inner 18B; the stop ring 55 whose inner periphery is contacted by the bearing member 56 is formed with the circular cross section, because the stop ring 55 is inhibited from deforming by being held by the bearing member 56; and the other stop ring 87 is formed with a rectangular cross section to prevent the stop ring 87 from coming off due to its deformation, and the rigidity of the stop ring 87 is accordingly increased.
  • the alignment structure in which the inner peripheral surface of the clutch inner 18B is in sliding contact with and held by the centre cam plate 30 enables oil which accumulates in the first and second depressed cams 51, 59 to be sufficiently supplied to the sliding-contact area between the centre cam plate 30 and the clutch inner 18B in such a way that oil is guided to the sliding-contact area between the centre cam plate 30 and the clutch inner 18B from the oil discharging passages 76, 77 provided in the outer peripheral edge portions of the first and second depressed cams 51, 59 which are made in the two sides of the disc part 30b of the centre cam plate 30.
  • the alignment structure can enhance the lubricity.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)

Claims (10)

  1. Système d'embrayage multidisque incluant :
    un embrayage extérieur (17) relié à un élément d'entrée (16) ;
    un embrayage intérieur (18A, 18B) relié à un élément de sortie (11) ;
    une pluralité de disques de friction d'entraînement (19) en prise avec l'embrayage extérieur (17) de façon à être mobiles dans une direction axiale et à être non rotatifs par rapport à l'embrayage extérieur (17) ;
    une pluralité de disques de friction entraînés (20) entrelacés avec les disques de friction d'entraînement (19), les disques de friction entraînés (20) étant en prise avec l'embrayage intérieur (18) de façon à être mobiles dans la direction axiale et à être non rotatifs par rapport à l'embrayage intérieur (18A, 18B) ;
    un plateau de pression (22) mobile dans la direction axiale afin d' amener les disques de friction d'entraînement (19) et les disques de friction entraînés (20) à se mettre en prise par friction en amenant les disques de friction d'entraînement (19) et les disques de friction entraînés (20) en contact par pression les uns avec les autres ;
    un ressort d'embrayage (23) pour solliciter le plateau de pression (22) dans un sens dans lequel le plateau de pression (22) amène les disques de friction d'entraînement (19) et les disques de friction entraînés (20) en contact par pression les uns avec les autres ; et
    un moyen d'assistance (24) pour augmenter une force de contact par pression du plateau de pression (22) lorsque le couple pour l'accélération est changé, caractérisé en ce que
    l'embrayage intérieur (18A, 18B), qui est mobile dans la direction axiale de l'élément de sortie (11), et le plateau de pression (22), qui est un élément différent de l'embrayage intérieur (18A, 18B), sont reliés ensemble pour être non rotatifs l'un par rapport à l'autre et être susceptibles d'être séparés l'un de l'autre dans la direction axiale de façon que, lorsque le moyen d'assistance (24) augmente la force de contact de pression du plateau de pression (22), le plateau de pression (22) est déplacé dans un sens amenant les disques de friction d'entraînement (19) et les disques de friction entraînés (20) en contact par pression les uns avec les autres tandis que l'embrayage intérieur (18A, 18B) est déplacé par rapport au plateau de pression (22) dans le même sens de façon à être détaché du plateau de pression (22).
  2. Système d'embrayage multidisque selon la revendication 1, caractérisé en ce que
    un moyen formant patin (25), pour diminuer la force de contact par pression produite par le plateau de pression (22) lorsque le couple pour le ralentissement est changé, est installé entre l'élément de sortie (11) et l'embrayage intérieur (18A, 18B) de façon que, en fonctionnement, le moyen formant patin (25) déplace le plateau de pression (22) dans un sens dans lequel le plateau de pression (22) diminue la force de contact par pression entre les disques de friction d'entraînement (19) et les disques de friction entraînés (20), l'embrayage intérieur (18) étant en contact intime avec le plateau de pression (22).
  3. Système d'embrayage multidisque selon l'une quelconque des revendications 1 et 2, caractérisé en ce que
    le moyen d'assistance (24) inclut :
    un ressort (48) configuré pour exercer une force élastique pour solliciter l'embrayage intérieur (18A, 18B) contre une force élastique du ressort d'embrayage (23) ; et
    un mécanisme à came (49) configuré pour déplacer de force l'embrayage intérieur (18A, 18B) contre la force de déplacement du ressort (48) pour augmenter la force de contact de pression produite par le plateau de pression (22) quand le couple pour l'accélération est changé.
  4. Système d'embrayage multidisque selon l'une quelconque des revendications 1 à 3, caractérisé en ce que
    l'embrayage intérieur (18A, 18B) inclut une partie cylindrique de mise en prise (18a) mettant en prise les disques de friction entraînés (20) avec sa périphérie extérieure,
    une partie cylindrique d'insertion (22b) insérée de façon coaxiale dans la partie cylindrique de mise en prise (18a) est prévue sur le plateau de pression (22),
    une pluralité de parties en saillie formant des rainures (37) dans lesquelles des rainures cannelées (38) sont respectivement formées, sont prévues sur l'une d'une périphérie intérieure de la partie cylindrique de mise en prise (18a) et d'une périphérie extérieure de la partie cylindrique d'insertion (22b), et
    une pluralité de parties en saillie de cannelure (39) en prise avec les rainures cannelées respectives (38) sont prévues sur l'autre de la périphérie intérieure de la partie cylindrique de mise en prise (18a) et de la périphérie extérieure de la partie cylindrique d'insertion (22b).
  5. Système d'embrayage multidisque selon la revendication 2, caractérisé en ce que
    l'embrayage intérieur (18A, 18B) et le plateau de pression (22) sont munis de parties formant butées plates (63, 64) s'étendant respectivement le long de plans orthogonaux aux axes de l'embrayage intérieur (18A, 18B) et du plateau de pression (22), de façon que les parties formant butée plates (63, 64) sont en contact l'une avec l'autre quand l'embrayage intérieur (18A, 18B) est amené en contact intime avec le plateau de pression (22).
  6. Système d'embrayage multidisque selon la revendication 5, caractérisée en ce que
    une pluralité de parties en saillie formant des rainures (37) dans lesquelles des rainures cannelées (38) sont respectivement formées sont prévues sur l'un de l'embrayage intérieur (18A, 18B) et du plateau de pression (22),
    une pluralité de parties en saillie de cannelure (39) en prise avec les rainures cannelées respectives (38) sont prévues sur l'autre de l'embrayage (18A, 18B) et du plateau de pression (22), et
    les parties formant butées (63, 64) sont prévues de façon qu'elles soient continues de manière unitaire jusqu'aux parties en saillie formant des rainures (37) et les parties en saillie de cannelure (39) pour s'étendre vers l'intérieur à partir des parties en saillie formant des rainures (37) et des parties en saillie de cannelure (39) dans une direction radiale.
  7. Système d'embrayage multidisque selon la revendication 4, caractérisé en ce que
    un premier passage d'huile (40) pour guider l'huile jusqu'à une zone de mise en prise entre les rainures cannelées (38) et les parties en saillie de cannelure (39) est prévu dans le plateau de pression (22) de façon à pénétrer dans la partie cylindrique d'insertion (22b) dans une direction radiale.
  8. Système d'embrayage multidisque selon l'une quelconque des revendications 4 et 7, caractérisé en ce que
    un second passage d'huile (41) pour guider l'huile jusqu'à une zone de mise en prise entre les rainures cannelées (38) et les parties en saillie de cannelure (39) est prévu dans le plateau de pression (22) de façon à pénétrer dans la partie cylindrique d'insertion (22b) dans la direction axiale.
  9. Système d'embrayage multidisque selon l'une quelconque des revendications 5 et 6, caractérisé en ce que
    des surfaces de contact par glissement (65, 66) sont respectivement fournies à l'embrayage intérieur (18A, 18B) et au plateau de pression (22) de façon à être en contact glissant l'un avec l'autre, les surfaces de contact par glissement (65, 66) étant continues jusqu'aux extrémités intérieures des deux parties formant butées (63, 64) s'étendant dans les directions radiales de l'embrayage intérieur (18A, 18B) et du plateau de pression (22), les surfaces de contact par glissement (65, 66) étant formées chacune en forme d'un arc autour d'une ligne d'axe central de l'embrayage intérieur (18A, 18B).
  10. Système d'embrayage multidisque selon la revendication 9, caractérisé en ce que
    des espaces (67, 68) sont formés entre les parties en saillie de cannelure (39) et l'une d'une périphérie intérieure d'une partie cylindrique de mise en prise (18a) et d'une périphérie extérieure d'une partie cylindrique d'insertion (22b), aussi bien que respectivement entre les parties en saillie formant des rainures (37) et l'autre de la périphérie intérieure de la partie cylindrique de mise en prise (18a) et de la périphérie extérieure de la partie cylindrique d'insertion (22b).
EP10251669.7A 2009-09-30 2010-09-28 Système à embrayage multi-disque Not-in-force EP2306038B1 (fr)

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EP2306038A3 EP2306038A3 (fr) 2014-02-19
EP2306038B1 true EP2306038B1 (fr) 2014-12-31

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JP4990254B2 (ja) * 2008-09-30 2012-08-01 本田技研工業株式会社 多板式クラッチ
JP4939585B2 (ja) * 2009-09-30 2012-05-30 本田技研工業株式会社 多板クラッチ装置
JP5854900B2 (ja) * 2012-03-16 2016-02-09 株式会社エフ・シー・シー 動力伝達装置
JP5439555B2 (ja) * 2012-08-08 2014-03-12 富士重工業株式会社 変速機
JP6753897B2 (ja) * 2018-07-27 2020-09-09 本田技研工業株式会社 パワーユニット
JP7209520B2 (ja) * 2018-12-05 2023-01-20 株式会社エフ・シー・シー 動力伝達装置
CN111255815A (zh) * 2020-01-17 2020-06-09 重庆隆鑫机车有限公司 强化离合器及发动机
US11209051B2 (en) * 2020-03-24 2021-12-28 Ford Global Technologies, Llc Clutch assembly pressure plate with tapered face

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JP4785668B2 (ja) 2006-08-02 2011-10-05 本田技研工業株式会社 多板クラッチ
JP4662896B2 (ja) * 2006-08-07 2011-03-30 本田技研工業株式会社 多板クラッチ
JP4805092B2 (ja) * 2006-10-25 2011-11-02 本田技研工業株式会社 多板式クラッチ装置
JP4797008B2 (ja) * 2007-09-26 2011-10-19 本田技研工業株式会社 多板クラッチ
JP5191819B2 (ja) * 2008-06-27 2013-05-08 本田技研工業株式会社 多板クラッチ
JP4939585B2 (ja) * 2009-09-30 2012-05-30 本田技研工業株式会社 多板クラッチ装置

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EP2306038A2 (fr) 2011-04-06
JP2011075035A (ja) 2011-04-14
EP2306038A3 (fr) 2014-02-19
US8490768B2 (en) 2013-07-23
US20110073432A1 (en) 2011-03-31
JP5171779B2 (ja) 2013-03-27

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